Hydraulic transmission system



July 2,1929. J. A. DIENNER HYDRAULIC 'ramsmssmu SYSTEM Filed March 10,1920 2 Sheets-Sheet l ki July 2, 1929. J. A. DIENNER HYDRAULIC TRANSMISS ION SYSTEM Filed March 10, 1920 2 Sheets-Sheet 2 firm/m) Glam 62/.17W

worms Patented July 2, 1929.

.rorlmmn 0! meme, rumors.

maamo MOI BYBTEI.

Application and 1min; 10, mo. Serial Io. sum.

M invention relates to washing machines and as particular reference toan improved and simplified transmission mechanism for connecting theelectric motor (or other source of power) with the washing niecha nismand with the wringer mechanism.

The invention is primarily directed to the end of providing an improvedsystem of ower transmission for washing machines which will dispensewith the necessity for all shafts and ears between the motor and thewasher and wringer mechanisms. The disadvantages of the shaft and gearsystem of transmlssion are numerous: First, the shaft and gear system oftransmission is inherently unsuited to deriving a periodically reversingrotation for the washer cylinder, such as is required in the reversingcylinder types of machines. This follows from the fact that aperiodically reversing motion having a point of zero motion at reverse,is not a natural function of any combination of gears and clutches. Y Asecond disadvantage of the shaft and gear system of transmission lies inthe fact that it is not adapted to effecting large speed reduc ions,such as are required between the drivin motor and the washer and wringermechanisms, without involving a large power loss and an objectionabledegree of noise and vibration.

A third disadvantage of the shaft and gear system of transmission is thefact that this form of transmission necessitates aligned bearingsbetween the different operating units of the machine. The necessity forthese aligned bearings contributes in a large measure to the assemblycost of the machine, and also to the maintenance cost, owin to thenecessity of re-aligning the bearings when making repairs or renewals ofworn and broken arts. From the fact that a domestic was ing machine mustessentially be of light weight and inexpensive construction, it willbeevident that the problem of mounting bearings and shafts on the machineand-maintaining them in alignment presents a considerable difliculty.The use of a heavy, rugged frame structure, possibly with the-additionof a mounting plate for supporting the various shaft bearings, resultsin a. construction which is exceedingly heavy and quite expensive tomanufacture. On the other hand, the use of a relatively light framestructure, such as of wood, upon which the bearings are directlymounted, results in a construction which is subject to distortion fromthe strains and vibrations developedin the machine, with the consequentdisa ignment and wear of the shafts and bearings. Furthermore, owin tothe requirement for accurately alignel hearings in this construction ofmachine, bench assembly of the several operating units is made imracticable, and consequentl these units an the entire machine, must hefloor assembled, which is a more diflicult and expensive operation.

The present form of transmission is a radical departure from thisprevious practice, and substantiall obviates the above disadvantages.Accor ing to the present invention, the transmission of ower is effectedentirely throu h a body of uid-in the nature of a h raulic transmission.This is accomplishe b utilizing the electric motor to drive a flui pumpwhich is adapted to circulate or pulsate a power transmitting fluidthrou h a fluid circuit or a closed fluid column. l nclnded in thisfluid circuit or column is a fluid motor which operates to drive thewasher mechanism under the power impulses transmitted through the bodyof fluid. Such system of transmission is uniquely adapted to deriving aperiodically reversing rotation for driving the washer mechanism. Byreason of the mobility of the bod of fluid, its small frictional lossand its sma 1 mass inertia, a periodically reversing direction of flowmay be mechanically imparted to the body of fluid with maximumefliciency and with the substantial elimination of all noise andvibration. In one embodiment of my invention, this reversing flow of thebody of fluid is accomplished by creating slow pressure pulsations inalternating directions, through the medium of a pulsator interposed inthe fluid column. The pressure pulsation of the fluid column in onedirection forces a volume of fluid through the fluid motor and therebyproduces a continuous rotation of the washer mechanism for a period ofseveral revolutions. Upon a reverse reciprocation of the pulsator, areverse ressure pulsation is created in the fluid co umn, therebyforcing a volume of the .fluid through the fluid motor 'in the reversedirection and resulting in a reverse rotation of the washer mechanismthrough a similar number of revolutions m the other direction. A furtherembodiment of this fluid transmission mechanism employing a plurality ofindependent fluid columns between the driving motor and the washermechanism, is described in the appended specification. The fluidtransmission mechanism between the electric motor and the wringermechanism preferably embodies the same general relation of fluid pumpand fluid motor connected b a closed fluid circuit, as above described.11 this transmission system, however, the flow is normallyuni-directional, so as to normally drive the wringer in one direction.The reversal of the drive to the wringer may be accomplished by areversing valve interposed in the fluid circuit or by a mechanicalreverse interposed in the mechanical connections.

A particular advantage residing in the use of fluid as the powertransmitting medium is the ability to effect large reductions in speedby simply proportioning the relative capacities of the fluid pump andfluid motor in the ratio of the desired speed reduction. For example, aspeed reduction of 1 to 40 may be obtained by simply proportioning thedisplacement capacities of the pump and motor in the ratio of 1 to 40.By utilizing this principle I am enabled to dispense with all gearing inthe transmission mechanism, with the consequent elimination ofsubstantially all noise and vibration, which is usually characteristicof reduction gearing.

A further advantage residing in the use of a body of fluid as the powertransmitting medium is the fact that all necessity for ali ed shafts andbearin s between the di erent operating unitso the machine is -therebyeliminated. This permits of a bench assembly of each of the operatingunits of the machine. Furthermore, in the event of breakage or wear ofany of the operating parts of the transmission mechanism a renewal ofthis operating part can be readily effected by the simple substitutionof the parts without requiring that the machine can be returned to thefactory for accurate alignment of the new operating unit with the restof the transmission mechanism. The maintenance and re air costs areconsequently very much simp ified and reduced, which is .a relativelyimportant factor in the case of washin machines, owing to the widedistribution 0 the machines and the practicaldifliculties involved inreturning the machines to the factory for repairs.

Referring to the accompanying drawings, wherein I have illustrated,various preferred constructions of my improved washing machine:

Figure 1 is. an end view of a Washing machine embodying my improvedfluid transmission mechanism, the end cover plate of the machine beingbroken away to illustrate the operative relation of the transmissionsystem;

Figure 2 is an enlarged longitudinal sectional view of the fluid controlvalve for the wringer motor;

Figure 3 is a transverse sectional view of the same, taken on the planeof the line 33 of Figure 2.

Figure 3 is a similar view taken on the plane of the line 3--3 of Figure2;

Figure 4 is a vertical sectional view of the fluid motor for driving thewringer.

Figure 5 is a View similar to Figure 1, illustrating a modified form oftransmission system for the washer mechanism.

Referring to Figure 1, the invention is illustrated as being embodied ina washing machine of the reversing cylinder type, although adaptationsto other types of Washing machines are also contemplated. It will beunderstood, of course, that the fluid. transmission mechanism for thewringer may be adapted to any type of machine.

The reversing cylinder which is indicated by the dotted circle 1, iscontained in a tank 2 mounted in a frame work constructed of angle iron,and comprising particularly the angle iron corner posts 3, which areprovided at their lower ends with suitable rollers 4. The transmissionmechanism is preferably supported at one end of the machine asillustrated, although it will be apparent that the mechanism may begrouped on one side-of the machine if desired. The tank 2 is notextended :entirel tothe wrin er end of the machine (whic is the end sown), but is spaced therefrom to provide an intervening space 10 inwhich is confined the transmission mechanism. An'outer facing plate 5,which is preferably removable or is hinged in order to be swung out ofthe way, is provided for covering the end of the machine and forenclosing the transmission mechanism. v

Referring first to the transmission system for the washer mechanism, ,itwill be obworm 8 supported at one side of the machine. This worm mesheswith a worm wheel 9, which operates to drive the short vertical shaft 11at a reduced speed. On the lower end of the shaft 11 is mounted a secondworm 12, which meshes with a second worm wheel '13 mounted verticallywith respect to the machine. The shaft of the worm wheel 13 is journaledin a bearing 14, which is supported on one of the cylinders of apulsator 15. This pulsator comprises a pair ofopposed cylinders 16 and17 which are mounted upon a common base 18. The base 18 is supportedupon brackets 1919, which are bolted to the corner legs 3. Upon theright hand cylinder 17 is mounted the electric motor 6. A bearingbracket 21 is provided for affording. bearin support for the end of themotor shaft 7, This bearing bracket may be mounted on the transverseframe members 22, or upon the pulsator structure similarly to thebearing 14.

Mounted for reciprocation in the opposed pulsator cylinders 16 and 17are the two plunger pistons 23 and 24, which are connected by the pistonrod 25. This piston rod has connect1on through a lateral pin 26 with aconnecting link 27, which has pivotal connection at its opposite endwith a crank pin 28 on the face of the worm wheel 13. Both of thepulsator cylinders 16 and 17 have communication with pipes 31 and 32respectively, which thread into port openings tapped in the heads of thecylinders. These pipes 31 and 32 extend up to the fluid motor 33, whichhas driving connection with the end trunnion of the cylinder 1.

The fluid motor 33 may be of any preferred type, being preferablypositive in action, however. I have illustrated a vane motor as beingthe preferred form of fluid motor, but I wish it to be understood that Ialso contemplate employing a rotary gear motor consisting of two meshinggear wheels, or a rotary eccentric motor, or practically any referredform of fluid motor which is suitable to the present adaptation. Thevane motor illustrated comprises an outer circular housing 34, which ismounted upon the frame structure of the machine, or upon a mountingplate at the end of the tank 2.

The housing 34 is closed ofl at front and rear by end plates, therebyforming a shallow cylindrical chamber, and journaled eccentrically inthis chamber is a rotor 36. The rotor shaft 37 is extended out throughthe rear wall of the housin 34 and has suitable driving connection withthe end trunnion of the cylinder 1. Formed inthe body of the rotormember 36 are a plurality of radial slots 38 in which are guided a plu-'rality of vanes 39. These vanes are normally impelled outwardly againstthe'walls of the housing 34 by compression springs 41 of suitable form,which are confined in the slots 38 in rearof the vanes. The periphery ofthe rotor member 36 is arranged to contact with the inner wall of thehousing 34'as indicated at 42. The fluid ports 43 and 44 which open into-the interior of the motor are disposed upon opposite sides of thispoint of contact 42 so as to cause a circulation of the motive fluidaround the rotor 36 and in contact with each of the rotor vanes 39. Thefluid pipes 31 and 32 have communication with the ports 43 and44'through a by-pass valvev45. This valve comprises a cylindrical ortapered valve member disposed in an outer housing in which are formedports and for the short worm shaftll.

. entirety the communicating with each of the pipes31 and 32, and alsowith the pipes leading to the fluid ports 43 and 44 of the motor. Formedin the periphery of the valve member is a pair of grooves 47-47,which-in one position of the valve-are adapted to place the ,ipes 31 and32 in communication with the uid ports 43 and 44 respectively. Extendingdiametrically through the body of the valve is a transverse port 48which, in the other position of the valve, is adapted to register witheach of the pi es 31 and 32 and by-pass the pressure pu sations aroundthe fluid motor, so that no rotation of the latter will result. Theshaft of the by-pass valve 45 is extended out through the end plate 5,where it is rovided with an operating handle 49 by which the operationof the washer mechanism may be controlled. This operation is as follows:

Assume that the control handle 49 has been thrown to the on position,and that the electric motor 6 has been started. The high speed rotationof the motor shaft 7 is firs t reduced through the worm 8 and worm wheel9, and is again reduced through the worm 12 and worm wheel 13 so thatthere is a comparatively slow reciprocation transmitted through theconnecting link 27 to the pistons 23 and 24. The speed of thisreciprocating motion is referably in the neighborhood of four or vereciprocations per minute. This slow reciprocating motion createsalternating pressure pulsations in the closed fluid column which is incircuit with the pulsator, and thereby induces a periodically reversingflow of fluid through the fluid motor 33. The action of thesealternating pressure pulsations is to revolve the fluid motor a numberof revolutions in one direction and then reverse the fluid motor andrevolve it an equal number of revolutions in the other direction.

The closed liquid column constitutes in its 0 hnder 17, the pipe 32, theinterior of the d uid motor 33, the pipe 31, and the other cylinder 16.This closed chamber is substantially filled with a suitable liquid,preferably a medium heavy grade of lubricating oil. The lubricatingqualities of the oil automatically insure the lubrication of all of theoperating parts which are included in the fluid column. It will beunderstood that, because of the slow reciprocation of the ulsator 15 thepressure surge of the fluid Into the fluid motor through either of theports 43 or 44 is at a relatively low velocity, but under considerablepressure. Consequently', the building up of pressure behind ea h of thevanes 39 is'comparatively slow, and as a result the fluid motor isrevolved at a relatively low speed, which is a desirable characteristicfor driving the washer cylinder 1. It should be noted that thevolumetric capacity of the fluid motor 33 is considerably smaller thanthat of either of the cylinders 16 or 17. The proportion is preferablyin the ratio of 1 to 4 or 1 to 5, whereby the entire pressure pulsationin one direction from one of the cylinders 16 or 17 will result in fouror five complete revolutions of the fluid motor.

It will be apparent that the reversal of the fluid motor 33 is effectedgradually and without shock; first, by reason of the dead center areasin the position of the crank pin 28, which insure a gradual building upof the fluid pressure and its gradual cessation before reversal; andsecond, b reason of the natural cushioning action 0 the oil column. Icontemplate increasing this cushioning property of the oil column byinterposing an air bubble in the column or by providing a suitable airtrap or pressure chamber in communication with the column.

Referring now to the fluid transmission mechanism for driving thewringer 50, it will be noted that on the other end of the shaft of theelectric motor 6 is coupled a small gear pump 51. This gear pumpconsists o a pair of small meshing spur gears enclosed in a tightlyfitting casing having intake and outtake ports aligned with the point ofintersection of the gears. I have illustrated the use of this type ofpump in the wringer transmission mechanism because 1. of the extremelysmall volumetric displace ment which it is possible to obtain in thesmall units of this type, and also because of its positive action, but Iwish it to be understood that I also contemplate employing a vane, orrotary eccentric type of pump, or even a centrifugal pumpf as I shallhereinafter describe. Leading rom the intake and Y outtake ports of thepump 51jare two pi es 52 and 53,-which extend up to a control va ve 54which is mounted in back of the end plate 5 and adjacent the top of themachine. The pipes 52 and 53 enter the valve housing at diametricallyopposite points; andextending from the valve housing at a pointintermediate the two ipes 52 and 53 are two pipes 55 and 56 which haveconnection with the fluid motor 57 for drivin the wringer 50. The fluidmotor 57 is pre erably of the rotary vane type, although, as remarked ofthe fluid motor 33, it might also be of the eccentric t e, or evenconsist of a large gear pump emp oyed in the relation of a fluid motor.This vane motor 57 is constructed similarly to the vane motor 33, andcomprises an outer circular housing 58, which is suitably bolted orotherwise secured on the side frame member of the wringer 50v J ournaledeccentrically in the housing 58 is the rotor 59, which is provided withits usual series of spring pressed vanes 61-61. The shaft 62 of therotor 59 has direct mechanical connection with the shaft of the lowerwringer roller 63, it being understood that both wringer rolls 63 arepositively geared together b gears enclosed in the gear housing 64. Tliefluid pipes 55 and 56 communicate with the interior of the motor housing58 through ports 65 and 66, which open into the motor housing uponopposite sides of the point of contact 67 of the rotor 59 with the motorhousing'58. The motor 57 is designed to have a relatively largevolumetric displacement, as compared with that of the gear pump 51, sothat a large speed reduction is eflected between the pump 51 and themotor 57. It will be ap arent that the displacement capacity of t emotor 57 will increase as the square of the diameter of the motorchamber and in direct ratio with the axial dimension of the motorchamber. By proportional increase in each dimension the capacity of themotor can thus be increased as the cube. Therefore, by designing themotor 57 of a comparatively large diameter and increasing the length ofthe motor chamber over that of ordinary stock design, the capacity ofthe motor can be made quite large without encumbering or obstructingaccess to the wringer rolls 63. The large capacity of the motor 57 incombination with the extremely small displacement capacity of the gearpum 51 insures the obtaining of a large spee reduction, whereby thewringer rolls 63 can be driven at their proper speed, which is generallyin the neighborhood of 35 or 40 revolutions per minute. i

The operation of the wringer and the direction of rotation of its rollsare controlled by the control valve 54, which is illustrated in sectionin Figures 2 and 3.

I Figure 2 represents a horizontal sectional view of the valve, and aswill be noted therefrom, the valve member 68 consists of a tapered valveplug which is enclosed in a tapered circular housing 69. The two fluidpipes 52 and 53 leading up from the pump 51 tap into the valve housing69 at diametrically opposite points in the vertical plane of the valveand at opposite ends of the valve plug 68. The two fluid pipes 55' and56 leading up to the motor 57 tap into the valve housin 69 in thehorizontal plane of the valve an at opposite ends thereof. The valveplug 68 is cored out hollow, as indicated at 70, and communicating withthis cored opening at o posite ends of the valve plug are the two va veports 71 and 72, which open out on opposite sides. of the valve plug 68.It will be apparent that when the valve plug 68 is put into a positionplacing the ports 71 and 72 in registration with the fluid pipes 52 and53, there will beat by-path circulation of the fluid from the pump 51through the central cored passage 70. In this position of the valve thefluid motor 57 is not in operation. In the same plane with the two valveports 71 and 72 are formed the valve, a shaft diagonal groove thediagonal groove two shallow grooves 73 and 74. Each of these groovesextends substantially 90 deg. about the circumference of the valve plug,the two grooves being displaced substantially 90 deg. from each' otherwith respect to the circumference of thevalve lug. The port 71 'isdisposed substantia y in the center of the groove 73. A third portopening 75 communicating with the cored passage is dis osed in the planeof the port opening 71 's latter port 0 ening being removed su tantially135 deg. rom the port opening 71. A fourth opening 76, communieatingwith the cored assage 70, is formed in the valve plug int e plane of theort opening 72. This latter port opening is ewlse removed approximately135 deg. from the port opening 72. Extending diagonally across thesurface of the valve is a groove 7 7 ,0 the riglllit 23131 engr of whichterminates sustantl y 5 e. omte rto ning 72. The an r e xtent of thegroov e 77 is approximate y 90 deg., so that the other end of the grooveterminates substantially 90deg. from the apparent that w en the valve,has been retated through 45 deg. in a clockwise direction A: kin 'atthe valve in the direction in- 'cated y the arrows in the section planesFigure 2) that the groove 73 will place the pipe 52 in directcommunication with the pipe 55,-and that the groove 74 will lace thepipe 53 in direct communication wi pipe- 54. As a result, there is adirect flow through the fluid motor 57. By rotatingthe valve through aproximately 135 deg. in a counterclockwise direction from the positionillustrated, it will be apparent that the port 75 will be brought intoregister with the pipe 55, and that the port 7 6 will be brought into reter with the pipe 53. Simultaneerewith, the left hand end of the 77 willbe revolved into communication with the pipe 52, and the right hand endwill be revolved into communication with the pipe 56. As a result,

ously circulation being from the pipe 52 through 57 to the pipe 56,thence through the motor 57, thence through the pipe 55, the port 75,the cored passage 70 and the port 76 to the ipe 53. For o rating F8 isextended om the valve lug out through the closed end of the valve ousing69, where it is provided with a nut 79 for maintaining a snug taperfitof the valve plu in its valve housing. An rating han It 80 is pinnedon the end of e shaft 78 on the outside of the'end plate 5. In Figure 5,I have illustrated a modified embodiment of fluid transmission mechanismfor driving the washer cylinder wherem the reversals are Qfiectfid byreversing gearing and are then transmitted to the washer it opening 75.'Itwill be the tor 143. This pulsator is the flow will be in a reversedirection, the

m through a synchronouslfiperato5 ing fluid transmission system. In formthe motor shaft 7 carries a worm 136, which meshes with a horizontalworm wheel 137. Theworm wheel 137 is mounted on a vertical shaft 138which has bearing sup ort in an upright bearing 139. This uprightbearing 139 is supported upon the horizontal mounting plate 84, as isalso the bearing bracket 141 for supporting the end of the motor shaft7.

Mounted on frame members 142 ad'acent the worm wheel 137 1 is a multi-cyder pulsator 143. This multi-cylinder ulsator is adapted to be drivenfrom the s aft 138 through the instrumentality of an automatic system ofreversing gearing 144. The particular form of reversing gearing shown isdisclosed in the patent to Phillips No. 1,077,748, issued November 4,1913, and comprises two facing bevel pinions 145, and an intermediatebevel gear 146. The two bevel pinions 145 are journaled for idlerotation on a sleeve 147, which is mounted in axial alignment with'theshaft 138 and is driven thereby. The pinions 145 are provided withprojecting clutch lugs which are adapted to cooperate with a rockingcluch bar 148, pivoted between pivotal projections, exten out from thesleeve 147. The locking clutch bar 148 revolves with the sleeve 147 andis adapted to be rocked into and out of alternating clutching engagementwith each of the bevel pinions 145. The rocking of the clutch bar 148occurs periodically under the action of a stud 149 on the face of thelarge bevel gear 146, which stud is adapted to alternately engage eachend of the clutch bar after a predetermined number of revolutions of thebevel gear 146.

The periodically reversing motion of the bevel gear 146 is transmittedthrough the crank shaft 151 into the interior of the crank case 152 ofthe multi-cylinder pulsaconstructed with preferably three cylinders 153all of which radiate from the central crank case 152 in the same plane.The fluid pulsator 143 is a substantial counterpart of the fluid motor154, a description of which will suflice to indicate the generalconstruction of the pulsator 143. .The fluid motor 154 comprises acircular crank case 155, which is mounted concentrically with the endtrunnion of the washer cylinder 1, and which is supported upon the endof the tank 2 or u on a su ta le supporting plate. Sp eqm.-d1stantli ingt 156. 'Reciprocating in the cylinders 156 are pistons 157 from whichextend connecting rods 158 having connection with a common crank in'thecrank shaft 159. The crank about the crank case 155 and radiat-.

erefrom are the three motor cylinders .12

shaft 159 is mechanically coupled with the end trunnion of the washercylinder 1 in an obvious manner.

In the heads of each of the cylinders 156 are provided ports which haveconnection through fluid pipes 161 with similar ports provided in theheads of the pulsator cylinders 153. Each of the pipes 161 is'filledwith oil to form a fluid transmission medium between the pistons of thepulsator 143 and the pistons of the motor 154. If desired, cushioningbubbles or pockets of air may be interposed in each of the fluid columns161. In the operation of the system, the rotation of the pulsator shaft151 in one direction produces successive outward strokes of each of thepulsator pistons progressively about the pulsator, thus pressureimpulses are imparted to each of the oil columns in progressive sequencein the order of the rotation of the pulsator 143. These pressurepulsations in the fluid columns act upon the pistons 157 of the fluidmotor in the same sequence as the rotation of the pulsator 143, andconsequently a synchronous rotation is imparted to the motor 143 and iscontinued as long as the pulsator 143 continues to revolve in the samedirection. Upon operation of the reversing gear mechanism 144, thedirection of rotation of the pulsator 143 is changed and the sequence ofthe pressure pulsations in the fluid columns 161 is accordinglyreversed. Immediately the progressive order of the inward strokes of thepiston in the motor 154 is reversed and the motor consequentl takes up areverse direction of rotation. t will therefore be seen that the fluid'motor 154 revolves in synchronism with the pulsator 143 at all times,revolving with the same rapidity of the pulsator 143 and reversing withthe pump at each operation of the reversing gear mechanism 144. Theprovision of three cylinders in each of the pulsator and motor unitsprevents any possibility of either unit becoming stalled on dead center.To stop the operation of the washer mechanism there is provided apositive clutch 162, interposed in the motor shaft 7, which is madecontrollable through a foot actuated control lever 163.

I do not intend to be limited to the particular details shown anddescribed, as they may obviously be extended and modified by thoseskilled in the art. It will be apparent that the transmission system maybe adapted to other types of machines than the reversing cylinder typeillustrated, such as to oscillating or dolly types of machines, and itwill therefore be understood that in the appended claim the term washermechanism is intended to include such other types.

I claim:

In hydraulic transmissionmechanism for translating continuousuni-directional rotary motion into rotary motion changing from forwardrotation to reverse rotation, the combination of a reversible fluidmotor capable of continuous rotary motion in either direction bydifference of fluid pressure, a source of power providinguni-directional rotary motion, a pulsator driven by said source ofpower, and means including a fluid column for transmitting difference influid pressure to said reversible fluid motor.

In witness whereof I hereunto subscribe my name this 18th day ofFebruary, A. D. 1920.

, OHN A. DIENNER.

